EP0684400A2 - Frein à disque à êtrier flottant - Google Patents

Frein à disque à êtrier flottant Download PDF

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Publication number
EP0684400A2
EP0684400A2 EP95111934A EP95111934A EP0684400A2 EP 0684400 A2 EP0684400 A2 EP 0684400A2 EP 95111934 A EP95111934 A EP 95111934A EP 95111934 A EP95111934 A EP 95111934A EP 0684400 A2 EP0684400 A2 EP 0684400A2
Authority
EP
European Patent Office
Prior art keywords
caliper
disc
elastic
elastic member
brake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP95111934A
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German (de)
English (en)
Other versions
EP0684400B1 (fr
EP0684400A3 (fr
Inventor
Hiroyuki Maeda
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Individual
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Individual
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Filing date
Publication date
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Publication of EP0684400A2 publication Critical patent/EP0684400A2/fr
Publication of EP0684400A3 publication Critical patent/EP0684400A3/xx
Application granted granted Critical
Publication of EP0684400B1 publication Critical patent/EP0684400B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/22655—Constructional details of guide pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/02—Release mechanisms

Definitions

  • the present invention relates to a floating caliper-disc type brake.
  • a floating caliper-disc type brake comprises a support fixed to non-rotatable portion of a vehicle, a caliper floatably supported by the support and an inner pad to be brought into contact with a piston which is slidably engaged in a cylinder formed in a rear arm of the caliper, an outer pad supported by a front arm of the caliper, wherein a disc rotating together with a wheel is clamped by the inner and outer pads to generate a breaking torque.
  • a gap between the disc and each pad, when the brake is released, is assured in the following manner.
  • a seal ring composed of rubber elastic body is interposed between the cylinder and the piston, wherein when the brake is applied, the piston is allowed to move in one direction to protrude from the cylinder owing to elastic deformation of the seal ring, and when the brake is released, the piston is moved in the other direction to return to be pushed into the cylinder owing to elastic restoration to the original form of the seal ring.
  • the seal ring is gradually varied in its retaining position with respect to the piston depending on wearing amount of both pads so that the piston is gradually moved in one direction to protrude from the cylinder. Consequently, amount of depression of a brake pedal, namely, amount of brake operating liquid is kept constant and a given gap is defined between the disc and the inner pad.
  • the outer pad When the outer pad is kicked back by the rotating disc, the outer pad is moved together with the caliper so as to be kept away from the disc, thereby defining a gap between the disc and the outer pad, at the time of release of the brake. At this time, caliper slightly floats relative to the support.
  • the present invention is made to solve the aforementioned problems of the conventional floating caliper-disc type brake and to provide a floating caliper-disc type brake comprising as follows.
  • the floating caliper-disc type brake comprises a support 4 fixed to non-rotatable portion of a vehicle, a caliper 5 floatably supported by the support 4 and having rear and front arms 5a and 5b, an inner pad 10 to be pushed by a piston 8, the piston 8 being slidably engaged in a cylinder 6 formed in the rear arm 5a of the caliper 5, an outer pad 14 supported by the front arm 5b of the caliper 5, at least one seal ring 12 which is interposed between the cylinder 6 and the piston 8 and is fixed to the rear arm 5a, and is retained slidably on a peripheral surface of the piston 8 wherein the retaining position is gradually varied depending on wearing amount of the inner and outer pads 10 and 14, wherein when the brake is applied, the piston 8 is pushed out from the cylinder 6 in one direction while elastically deforming the seal ring 12 within deformable amount of the seal ring 12, and the caliper 5 is moved to the other direction with respect to the support 4, so that the inner and
  • a floating caliper-disc type brake according to a second aspect of the invention includes a two port type cylinder 6.
  • a floating caliper-disc type brake according to a third aspect of the invention includes dual wheels.
  • a floating caliper-disc type brake according to a fourth aspect of the invention includes a plurality of elastic members 18 (28a, 28b).
  • a floating caliper-disc type brake includes a plurality of elastic members 18 (28a; 28b) which are arranged at both sides of the caliper in a peripheral direction of the disc 1.
  • a floating caliper-disc type brake according to a sixth aspect of the invention includes a direct active type bearing 24 interposed between the support 4 and the caliper 5 for supporting floating of the caliper 5.
  • a floating caliper-disc type brake according to a seventh aspect of the invention includes a plurality of direct active type bearings 24 which are interposed between the support 4 and the caliper 5 at both sides of the caliper 5 in a peripheral direction of said disc 1.
  • the inner pad 10 is pressed against one side surface of the disc 1 to generate repulsive force by which the caliper 5 is moved in the other direction so that the outer pad 14 is pressed against the other side surface of the disc 1.
  • the elastic member 18 (28a, 28b) are elastically deformed by the second length L 2 .
  • the seal ring 12 is elastically restored to the original form (hereinafter referred to as simply elastically restored) so that the piston 8 is moved in the other direction to return to the original position (hereinafter referred to as simply as moved to return) by the first length L 1 so that a gap is defined between the inner pad 10 and one side surface of the disc 1.
  • the retained elastic member 18 (28a, 28b) are elastically restored.
  • the caliper 5 is moved to return in one direction by the second length L 2 so that a second gap 6 is defined between the outer pad 14 and the disc 1.
  • the second gap 6 is equal to the second length L 2 which is elastic restoration amount of the elastic member 18 (28a, 28b).
  • the second length L 2 by which the caliper 5 is moved to return when the brake is released is set to be smaller than the first length L 1 regardless of the wearing amount of the outer pad 14. Accordingly, the first gap A is surely defined between the inner pad 10 and the disc 1 in a state where the second gap 6 is defined between the outer pad 14 and the disc 1, thereby satisfactorily prevent dragging of the disc 1 into both pads 10 and 14.
  • an excellent elastic restoration can be obtained by a plurality of elastic members 18 (28a, 28b).
  • an excellent elastic restoration by a plurality of elastic members 18 can be obtained at both sides of said caliper 5 in a peripheral direction of said disc 1. Accordingly, the caliper 5 can be smoothly moved to return with respect to the support 4 by the length L 2 .
  • the floating of the caliper 5 with respect to the support 4 can be performed smoothly by a direct active type bearing 24. Accordingly, the caliper 5 can be moved to return in one direction by the exact second length L 2 owing to the elastic restoration amount of the elastic member 18 (28a, 28b). As a result, the second gap 6 can be surely defined between the outer pad 14 and the disc 1 when the brake is released.
  • the caliper 5 can be moved to return more smoothly with respect to the support 4.
  • FIG. 1 A floating caliper-disc type brake according to a first embodiment of the present invention will be described now with reference to Figs. 1 to 6.
  • a discoidal disc 1 is fixed to a rotatable member of a vehicle such as a wheel hub, a flange of an axle shaft which is rotated together with a wheel, not show, by way of bolts and nuts.
  • the wheel includes not only a single wheel but also dual wheels comprising a pair of wheels.
  • a support 4 is firmly fixed to a non-rotatable portion of the vehicle such as a knuckle and an axle tube, not shown.
  • a caliper 5 bridging over the disc 1 is supported by the support 4 to float (hereinafter referred to as floatably supported) in one direction (in a direction of axis of rotation of the disc 1, i.e. to the left and right in Fig. 1).
  • a cylinder 6 is provided in a rear arm 5a of the caliper 5 (at one end of the caliper 5 in a direction of axis of rotation of the disc 1).
  • the caliper 5 is guided by a pair of pins 16 and moved in a direction of axis of rotation of the disc 1 since the pair of pins 16 are arranged in parallel with the support 4 and floatably engaged in holes 15a of ears 15 provided at both sides of the caliper 5 in a rotating direction (peripheral direction) of the disc 1.
  • the cylinder 6 may be formed of a two port type.
  • a piston 8 is engaged in the cylinder 6 provided in the rear arm 5a of the caliper 5 so as to slide in the direction of axis of rotation of the disc 1 by way of a seal ring 12 as shown in Figs. 2 to 4. It is a matter of course that a plurality of seal rings may be provided to obtain the same function.
  • An inner pad 10 is brought into contact with the piston 8 so as to be pushed by the piston 8.
  • An outer pad 14 is brought into contact with and supported by a front arm 5b of the caliper 5 (other end of the caliper 5 in the direction of axis of rotation of the disc 1).
  • the outer pad 14 may be integrally attached to the front arm 5b by way of a detachable coupling means such as a bolt.
  • Each of a pair of pins 16 fixed to the support 4 comprises, as shown in Fig. 1, an axle member 16a penetrating the support 4 and a bush 16b fixed to the axle member 16a, wherein the hole 15a of the ear 5 of the caliper 5 floats relative to the outer peripheral surface of the bush 16b.
  • a pair of direct active type bearings 24 are interposed between the bush 16b and the hole 15a respectively at a portion where the hole 15a moves relative to the bush 26 so as to reduce a moving resistance of the caliper 5 with respect to the support 4, thereby allowing the caliper 5 to move smoothly.
  • Denoted at 20 and 21 are sealing boots for respectively covering each end portion of the ear 15 of the caliper 5 and of the bushes 16b.
  • Each elastic member 18 is interposed in each pin 16 of the support 4, namely, between each bush 16b and each ear 15 of the caliper 5 and disposed at a position avoiding a direct active type bearing 24 as shown in Figs. 1 and 5.
  • the elastic member 18 is formed annularly and made of a rubber elastic body (rubber or elastomer) and a plurality of elastic members 18 are disposed in each pin 16.
  • the elastic member 18 allows the caliper 5 to move in the other direction while it is deformed within deformable amount of the elastic member 18.
  • the elastic member 18 allows the caliper 5 to move to return in one direction. Namely, when the brake is released, the elastic member 18 is elastically restored from a state as shown in Fig.
  • a plurality of annular grooves 22 are defined in the ears 15 of the caliper 5 and an outer periphery of the elastic member 18 is embedded into each annular groove 22, and then an inner peripheral surface of each elastic member 18 is elastically brought into contact with an outer peripheral surface of each pin 16.
  • a shallow annular groove portion 22a is defined in the inner periphery of the annular groove 22 as shown in Fig. 5, wherein the elastic member 18 is allowed to be elastically deformed in the shallow annular groove portion 22a and floating of the caliper 5 is performed precisely at the side of the hole 15a.
  • Elastic restoration amount of the elastic member 18, namely, the second length L 2 by which the caliper 5 is moved in one direction is set to be smaller than the first length L 1 which is elastic restoration amount of the seal ring 12, namely, the second length L 2 is set to be one fifth to four fifths of the first length L 1 and is preferable to be set to be the half of the first length L i .
  • a plurality of elastic members 18 are disposed between each pin 16 and the ear 15 of the caliper 5 in the direction of axis of rotation of the disc 1 so as to generate a large elastic restoring force depending on the weight of the caliper 5. If the caliper 5 can be moved to return in one direction, or single elastic member 18 alone can be disposed in each pin 16.
  • each elastic member 18 Since the hole 15a floats with respect to each pin 16 when the brake is applied, each elastic member 18 is deformed by the second length L 2 as shown in Fig. 6.
  • the outer pad 14 is worn by an amount exceeding a given amount, relative moving amount between the pin 16 and the hole 15a largely exceeds a given amount so that the caliper 5 and elastic member 18 are moved in the other direction with respect to each pin 16, whereby a retaining position of each elastic member 18 with respect to each pin 16 is gradually varied depending on the wearing amount of the outer pad 14.
  • the seal ring 12 is elastically restored so that the piston 8 is moved to return in the other direction by the first length L 1 , so as to be pushed into the cylinder 6 thereby defining a gap between the inner pad 10 and one side surface of the disc 1.
  • each elastic member 18 is elastically restored.
  • the caliper 5 is moved to return in one direction by the second length L 2 so as to define the second gap 6 between the outer pad 14 and the disc 1.
  • the second gap 6 is equal to the second length L 2 which is the elastic restoration amount of the elastic member 18.
  • the caliper 5 Since the direct active type bearing 24 is interposed between the bush 16b and the hole 15a, the caliper 5 is smoothly moved with respect to the support 4, without generating moving resistance based on the elastic restoration of each elastic member 18, thereby assuring the returning of the caliper 5 by the second length L 2 .
  • the second length L 2 by which the caliper 5 is moved to return in one direction when the brake is released is set to be smaller than the first length Li.
  • the first gap A is defined between the inner pad 10 and the disc 1 with assurance so that the disc 1 is prevented from being dragged in both inner pad 10 and outer pad 14.
  • the second length L 2 is set to be one fifth to four fifths of the first length L1
  • the first and second gaps A and 6 are suitably defined to prevent the disc 1 from being dragged in both inner pad 10 and outer pad 14.
  • the second length L 2 is set to be the half of the first length L 1
  • the first and second gaps A and 6 are defined by the same length so as to satisfactorily prevent the disc 1 from being dragged in both inner pad 10 and outer pad 14. Even if the elastic member 18 is fixed to each pin 16 at the inner periphery thereof and it is brought into contact with or retained by the hole 15a of the caliper 5 at the outer periphery thereof, the same function is obtained.
  • a floating caliper-disc type brake according to a second embodiment will be described with reference to Figs. 7 to 9.
  • the second embodiment as well as third and fourth embodiments, described later, are substantially the same as the first embodiment except elastic members, and other elements of the second to fourth embodiments are the same as those of the first embodiment, and hence numerals denoted at those elements are denoted at the same numerals. That is, the second to fourth embodiments relate to first to third modifications of the structure of the elastic member.
  • Figs. 7 to 9 show an example of a first modification of a structure of the elastic member.
  • Elastic members 28a and 28b disposed between each pin 16 of the support 4 and the hole 15a of the ear 15 of the caliper 5 are respectively made of spring steels. It is possible to use elastic members 28a and 28b instead of a rubber elastic material since they are not necessary to perform liquid sealing between each pin 16 and each ear 15 of the caliper 5.
  • Elastic members 28a are respectively fixed to each pin 16 of the support 4 in a given interval and a single elastic member 28b is fixed to the ear 15 of the caliper 5.
  • the elastic members 28a and 28b define the second gap 6 between the disc 1 and the outer pad 14 so as to allow the caliper 5 to move to return in one direction by the second length L 2 when the brake is released.
  • Each of the elastic members 28a and 28b is formed annularly wherein the outer periphery portion of each elastic member 28a can be retained by the inner periphery portion of the single elastic member 28b in a given width.
  • Slits 28c and 28d are defined on the elastic members 28a and elastic member 28b circumferentially in a given interval so that the elastic members 28a and 28b can be easily deformed. Accordingly, the elastic members 28a and 28b are elastically deformed between the slits 28c and 28d.
  • Each interval between the elastic members 28a is set in such a way that one of the elastic members 28a is always retained by the other elastic member 28b when the brake is applied, and amount of moving of the caliper 5 to return to an original position (hereinafter referred to as return moving amount) involved in retaining of the elastic member 28a by the other elastic member 28b, namely, the second length L 2 which is the elastic restoration amount of the elastic members 28a and 28b is smaller than the first length L 1 which is the elastic restoration amount of the seal ring 12 regardless of the wearing amount of the outer pad 14 when the brake is released, and it is set to be one fifth to four fifths of the first length L, and is preferable to be set to be about the half of the first length L, .
  • the seal ring 12 is elastically restored to so that the piston 8 is moved to return in the other direction by the first length L 1 so as to define a gap between the inner pad 10 and one side surface of the disc 1.
  • each of the retained elastic members 28a and 28b is elastically restored.
  • the caliper 5 is moved to return in one direction by the second length L 2 so as to define a second gap 6 between the outer pad 14 and the disc 1.
  • the second gap 6 is equal to the second length L 2 which is the elastic restoration amount of the retained elastic members 28a and 28b.
  • the second length L 2 by which the caliper 5 is moved to return when the brake is released is set to be smaller than the first length L 1 regardless of the wearing amount of the outer pad 14.
  • the first gap A is surely defined between the inner pad 10 and the disc 1 in a state where the second gap 6 is defined between the outer pad 14 and the disc 1, so that the disc 1 is satisfactorily prevented from being dragged in both inner pad 10 and outer pad 14.
  • the second length L 2 is set to be one fifth to four fifths of the first length L 1
  • the first and second gaps A and 6 are suitably defined to prevent the disc 1 from being dragged in both inner pad 10 and outer pad 14.
  • the second length L 2 is set to be about the half of the first length L 1
  • the first and second gaps A and 6 are defined by substantially the same length so as to satisfactorily prevent the disc 1 from being dragged in both inner pad 10 and outer pad 14.
  • the elastic members 18, elastic members 28a and 28b are disposed between each pin 16 of the support 4 and each ear 15 of the caliper 5, they can be interposed between exclusive members provided between the support 4 and the caliper 5 instead of the each pin 16 and ear 15 for performing the same function as the first and second embodiments.
  • one elastic member 18 the elastic members 28a and 28b are paired
  • the present invention is also applicable to a floating caliper-disc type brake wherein the caliper 5 is slidable relative to the groove (at both sides of the caliper 5 in a peripheral direction of the disc 1) of the support 4.
  • the elastic member 18, elastic members 28a and 28b are not limited to have annular shapes but they can have a rectangular shape or other shapes.
  • a floating caliper-disc type brake according to a third embodiment showing a second modification of the elastic member will be described with reference to Fig. 10 and 11.
  • the elastic member 18 comprises an inner cylinder 30 formed of a metallic cylindrical member and an elastic material 31 made of a rubber elastic body which is vulcanized and adhered to the outer peripheral surface of the inner cylinder 30.
  • the inner cylinder 30 includes protruding piece portions 32 and 33 extending radially at a part thereof and tip ends of the protruding piece portions 32 and 33 are positioned at an inner surface of the hole 15a. More in detail, the inner cylinder 30 has the protruding piece portions 32 and 33 at both ends thereof in the direction of a central axis thereof.
  • the protruding piece portion 32 at one end of the inner cylinder 30 is formed at the tip end of a tapered portion 35, which is formed by gradually enlarging one end of the inner cylinder 30 in the diameter of the inner cylinder 30 by bending protruding pieces remained on one end of the inner cylinder 30 in the direction of the outer diameter of the inner cylinder 30.
  • four protruding piece portions 32 are formed circumferentially in the same interval.
  • the protruding piece portion 33 at the other end of the inner cylinder 30 is formed by bending protruding pieces remained on the other end of the inner cylinder 30 in the direction of the outer diameter of the inner cylinder 30.
  • four protruding piece portions 33 are formed circumferentially in the same interval.
  • the elastic material 31 may be subjected to vulcanization and adhered to the side surfaces of the protruding piece portions 32 and 33 but a mold release agent may be applied previously to the protruding piece portions 32 and 33 to prevent the elastic material 31 from being vulcanized and adhered to the protruding piece portions 32 and 33 so that they may be formed individually separately from the elastic material 31 so as to be elastically deformed. If the adhesion between the elastic material 31 and the protruding piece portions 32 and 33 is prevented, the elastic deforming force of the elastic material 31 can be maintained constant for a long period of time.
  • a surface layer 31 a of the circumferential surface of the elastic material 31 forming the elastic close adhering surface (retaining surface) is subjected to a process for adjusting a friction coefficient.
  • a process for adjusting a friction coefficient it is general to lower the friction coefficient.
  • the surface layer 31 a is cured by heating the surface layer of the elastic material 31 so as to thermally deteriorate it or by applying chemicals on the surface layer 31 a so as to deteriorate it.
  • Such an elastic member 18 may be interposed between the pin 16 of the support 4, namely, between the bush 16b and the ear 15 of the caliper 5 at a position avoiding the direct active type bearing 24. It is also possible to attach a cylindrical bush to the hole 15a of each ear 15 so as to adjust the friction coefficient between the hole 15a and the surface layer 31 a of the elastic material 31, whereby the inner peripheral surface of each hole 15a can be formed by the bush. At that time, if the elastic member 18 is pressed into and fixed to each pin 16 of the support 4, each bush 16b of each pin 16 can be omitted.
  • the elastic member 18 is pressed into and fixed to each pin 16 of the support 4. At this time, the elastic member 18 is pressed into each pin 16 from one end side of the inner cylinder 30. Since the tapered portion 35 is formed at one end of the inner cylinder 30, the pin 16 is received easily from one end of the inner cylinder 30 so as to press the elastic member 18 into each pin 16. Since the protruding piece portion 33 is formed at the other end of the inner cylinder 30, the elastic member 18 can be easily pressed into the pin 16 by putting a jig to each protruding piece portion 33.
  • Each pin 16 is inserted into each hole 15a of the caliper 5 while slightly compressing the elastic material 31 in a state where the elastic member 18 is pressed into each pin 16 of the support 4 at a given position thereof.
  • the circumferential portion of the elastic material 31 strikes against an insertion side end of the hole 15a of the caliper 5 so that the elastic material 31 is liable to be damaged.
  • a chamfering portion 15b is previously formed at the peripheral edge of the insertion side end of the hole 15a as shown in Fig. 10. Accordingly, the elastic material 31 is guided along the chamfering portion 15b at the surface thereof, and it is inserted into the hole 15a while it is compressed gradually. As a result, the elastic material 31 can be elastically compressed by a given amount without being damaged, and can be retained by the hole 15a.
  • the elastic member 18 Since the inner cylinder 30 is pressed into and fixed to each pin 16 in a state where the elastic member 18 is mounted between each pin 16 of the support 4 and each hole 15a of the caliper 5, the elastic member 18 is not moved with respect to each pin 16 when the brake is applied.
  • the protruding piece portions 32 and 33 define slight gaps between them and the inner surface of each hole 15a or slidably contact the inner surface of each hole 15a.
  • the hole 15a of the caliper 5 is moved with respect to each pin 16 so that the elastic material 31 of each elastic member 18 is elastically deformed by the second length L 2 in the same way as the first embodiments as shown in Fig. 6.
  • the elastic deformation of the elastic member 18 by the second length L 2 is caused by a friction force between the elastic material 31 and the inner surface of each hole 15a.
  • the protruding piece portions 32 and 33 are also elastically deformed appropriately.
  • the elastic deforming amount of the elastic material 31 by the second length L 2 can be precisely determined by increasing or decreasing, namely, adjusting the friction force generated between the elastic material 31 and the inner surface of each hole 15a in the manner of adjusting the friction coefficient between the elastic material 31 and the inner surface of the hole 15a.
  • the elastic material 31 of each elastic member 18 and the protruding piece portions 32 and 33 are elastically restored.
  • the caliper 5 is moved to return in one direction by the second length L 2 so as to define the second gap 6 between the outer pad 14 and the disc 1.
  • the second gap 6 is equal to the second length L 2 which is the elastic restoration amounts of the elastic material 31 of the elastic member 18 and that of the protruding piece portions 32 and 33.
  • the elastic restoration force of the elastic material 31 can be adjusted by appropriately selecting elastic coefficient, hardness, length in the central axial direction, thickness in the radial direction, etc. of the elastic material 31.
  • each of the protruding piece portions 32 and 33 provided at both ends of the inner cylinder 30 defines a slight gap between it and the inner surface of each hole 15a or slidably contacts the inner surface of each hole 15a. Accordingly, when the caliper 5 is largely moved vertically relative to the vehicle accompanied by bound or rebound of the vehicle during traveling of the vehicle, each of the protruding piece portions 32 and 33 are brought into contact with the inner surface of each hole 15a so as to restrain the caliper 5 from being moved relative to the pin 16. As a result, it is possible to restrain a par t of the elastic material 31 (mainly an upper end portion thereof when mounted on the vehicle) from being deformed excessibly, and also possible to satisfactorily restrain the elastic material 31 from being plastically deformed early. Accordingly, each of the protruding piece portions 32 and 33 may be formed on the elastic material 31 only at a portion where the elastic material 31 is easily plastically deformed (an upper end portion of the elastic material 31 when mounted on the vehicle).
  • the direct active type bearing 24 can be omitted. Further, the same function can be obtained even if the former is replaced by the latter, and the metallic outer cylinder is pressed into and fixed to the hole 15a of the ear 15, and then the inner peripheral surface of the elastic material composed of rubber elastic body which is subjected to vulcanization and adhered to the inner peripheral surface of the metallic cylinder is elastically brought into contact with each pin 16.
  • Fig. 12 shows a modification of the structure of the elastic member of the third embodiment.
  • the inner cylinder 30 includes protruding piece portions 32 and 33, and a protruding piece portion 34 wherein a curved portion 33a is formed on an outer diameter portion of the protruding piece portion 33.
  • the protruding piece portion 34 is formed by cutting (in a shape not forming a straight line such as an M-shape, U-shape, V-shape) a part of the inner cylinder 30 (a middle portion in a central axial direction), and erecting the cut portion in a direction of the outer diameter thereof, wherein the height of the erected portion, i.e.
  • protruding piece portion 34 in a radial direction is the same as those of the protruding piece portions 32 and 33 of the second modification as illustrated in Figs. 10 and 11.
  • a plurality of protruding piece portion 34 may be formed in a central axial direction or circumferentially.
  • the curved portion 33a provided at the protruding piece portion 33 is formed by bending the outer peripheral portion of the protruding piece portion 33 toward the elastic material 31, and it is slightly longer in a radial direction (substantially the same as the outer diameter of the elastic material 31 when it is not compressed as shown in Fig. 12), and further it is elastically pressed against a tapered portion 31 b formed on the outer peripheral portion of the elastic material 31.
  • the curved portion 33a contacts a peripheral edge of the insertion side end of the hole 15a of the ear 15 and the elastic material 31 is inserted into the hole 15a while the protruding piece portion 33 and the tapered portion 31 b are elastically reduced in height in a radial direction. Accordingly, the elastic material 31 can be inserted into the hole 15a without being scarcely damaged while it is compressed elastically in a given amount. As a result, the chamfering portion 15b of the ear 15 as shown in Fig. 10 can be omitted.
  • the protruding piece portion 34 provided on the middle portion of the inner cylinder 30 in the central axial line thereof can function in the same way as the protruding piece portions 32 and 33 of the second modification as shown in Figs. 10 and 11.
  • a floating caliper-disc type brake according to a fourth embodiment showing a third modification of the elastic member will be described with reference to Figs. 13 and 14.
  • the elastic member 18 comprises a metallic inner cylinder 40, a metallic outer cylinder 41, a main elastic material 42 serving as inner elastic material composed of rubber elastic body which is subjected to vulcanization and adhered between an outer peripheral surface of the inner cylinder 40 and an inner peripheral surface of the outer cylinder 41, and an auxiliary elastic material 43 composed of rubber elastic body which is subjected to vulcanization and adhered to an outer periphery of the outer cylinder 41.
  • the outer cylinder 41 can be contracted or the inner cylinder 40 can be expanded after vulcanisation of the rubber elastic body so as to prevent the residual stress from being generated inside the main elastic material 42 to thereby weaken the adhesion owing to shrinkage after vulcanization of the rubber elastic body. It is possible to press the main elastic material 42 into a space between the inner cylinder 40 and the outer cylinder 41 while the main elastic material 42 is not adhered to at least one of the inner cylinder 40 and outer cylinder 41.
  • the main elastic material 42 has a main function to be deformed by the second length L 2 when the brake is applied and to allow the caliper 5 to move to return in one direction by the second length L 2 when the brake is released.
  • the elastic restoration force of the main elastic material 42 can be adjusted by appropriately selecting elastic coefficient, hardness, length in the central axial direction, thickness in the radial direction, etc. of the main elastic material 42.
  • the auxiliary elastic material 43 contacts the inner peripheral surface of the hole 15a of each ear 15 with a given friction force and has a main function to elastically deform the main elastic material 42 by the second length L 2 when the brake is applied.
  • the auxiliary elastic material 43 is formed thin (thickness of 1 mm or less) on the surface of the outer cylinder 41 and made of a rubber elastic body having a given hardness so as to generate friction force between it and the inner surface of each hole 15a of the caliper 5.
  • the elastic member 18 is assembled in the manner that the inner cylinder 40 is pressed into and fixed to each pin 16 of the support 4, then the auxiliary elastic material 43 is elastically brought into close contact with or retained by the inner peripheral surface of the hole 15a of the ear 15. It is possible to form a tapered portion, like the tapered portion 35 in the third embodiment, on one end of the inner cylinder 40 to facilitate the pressing operation of the inner cylinder 40 into each pin 16. Further, it is possible to form the same tapered portion 15b as the third embodiment on the insertion side end of the hole 15a of the caliper 5 to facilitate the inserting operation of each pin 16 into the hole 15a of the caliper 5. When the elastic member 18 is inserted into the hole 15a of the caliper 5, the main elastic material 42 interposed between the inner cylinder 40 and the outer cylinder 41 is not deformed and only the auxiliary elastic material 43 is compressed.
  • each elastic member 18 Since the inner cylinder 40 is pressed into and fixed to each pin 16 of the support 4, each elastic member 18 is not moved with respect to each pin 16 when the brake is applied. Further, the auxiliary elastic material 43 is elastically brought into contact with the inner surface of the hole 15a of the caliper 5.
  • the main elastic material 42 is elastically deformed by the second length L 2 as shown in Fig. 6 owing to the friction force between the auxiliary elastic material 43 and the inner surface of each hole 15a. Since the auxiliary elastic material 43 is thin, it is scarcely moved in the central axial direction thereof. Accordingly, it is possible to precisely generate the elastic deforming amount by the second length L 2 in the main elastic material 42 by adjusting the friction coefficient of the auxiliary elastic material 43 (or the bush attached to the inner periphery of the hole 15a to which the auxiliary elastic material 43 is elastically brought into contact).
  • the auxiliary elastic material 43 has a main function to contact the peripheral surface of the hole 15a to generate a precise friction force, it can be made of a rubber elastic body having a given hardness and formed separately from the main elastic material 42, thereby generating the precise friction force. Accordingly, it is possible to allow the elastic member 18 to have an arbitrary length in the central axial direction and allow the auxiliary elastic material 43 to directly contact the inner surface of the hole 15a of the metallic caliper 5. It is possible to attach a bearing alloy on the inner surface of the hole 15a of the caliper 5 by plating so as to adjust the friction coefficient, namely, to increase or decrease the friction coefficient between the auxiliary elastic material 43 and the inner surface of each hole 15a.
  • the main elastic material 42 and the auxiliary elastic material 43 are respectively made of separate members adapted for performing their own functions. Further, when the brake is applied, it is possible to elastically deform the main elastic material 42 by the second length L 2 as shown in Fig. 6 owing to the friction force generated between the auxiliary elastic material 43 and the inner surface of each hole 15a. If the outer pad 14 is worn by an amount exceeding a given amount, the auxiliary elastic material 43 is slid with respect to the inner surface of each hole 15a while the elastic deforming amount of the main elastic material 42 is maintained by the second length L 2 , thereby gradually varying the retaining position of the auxiliary elastic material 43 with respect to the inner surface of each hole 15a depending on the wearing amount of the outer pad 14. When the brake is released, the main elastic material 42 is elastically restored, thereby moving the caliper 5 to return by the second length L 2 so as to define the second gap 6 between the outer pad 14 and the disc 1.
  • the interval between the inner and outer cylinders 40 and 41 is varied.
  • the spring constant in the direction perpendicular to the central axis (in a radial direction) is greater than that in the central axial direction so that the variation of the interval between the inner and outer cylinders 40 and 41 is satisfactorily restrained as an entire elastic deformation of the main elastic material 42.
  • a part of the main elastic material 42 (mainly an upper end portion thereof when mounted on the vehicle) is restrained from being deformed excessively in the radial direction so that the main elastic material 42 is satisfactorily restrained from being plastically deformed early.
  • the auxiliary elastic material 43 has a given hardness and thin thickness, even if permanent set in fatigue is generated in a part thereof (mainly an upper end portion thereof when mounted on the vehicle), the close contact between the auxiliary elastic material 43 and the inner surface of the hole 15a of the caliper 5 can be maintained satisfactorily as a whole.
  • the direct active type bearing 24 interposed between the bush 16b and the hole 15a can be omitted. Further, if the bush having a given friction force is attached to the hole 15a and the outer cylinder 41 is slidably retained by the bush in a given friction force, the auxiliary elastic material 43 can be omitted.
  • auxiliary elastic material 43 is subjected to vulcanization and adhered to the inner cylinder 40 and the outer cylinder 41 is pressed into and fixed to the hole 15a of the caliper 5 wherein the auxiliary elastic material 43 is elastically brought into contact with each pin 16.
  • each elastic member 18 is disposed between each pin 16 of the support 4 and the ear 15 of the caliper 5.
  • single or plural elastic members 18 can be disposed between exclusive members, which are separately formed the pin 16 and ear 15, instead of each pin 16 and ear 15, thereby obtaining the same function as those of the aforementioned embodiment.
  • the elastic member 18 is mounted between each pin 16 of the support 4 and each ear 15.
  • the inner cylinder 30 is pressed into and fixed to one of pins integrated with the caliper 5 or holes of the support 4, and the elastic material 31 is slidably brought into contact with the other of pins integrated with the caliper 5 or the holes of the support 4 respectively in a given friction force, the same function can be obtained.
  • the elastic member 18 is mounted between each pin 16 of the support 4 and each hole 15a of the caliper 5.
  • the elastic member 18 is mounted between a pin integrated with the caliper 5 and a hole of the support 4, the same function can be obtained.
  • the gap is surely defined between the disc and both pads when the brake is released.
  • the outer pad can be prevented from being always slid with respect to the disc, thereby preventing the outer pad from generating dragging torque therein. Consequently, it is possible to improve fuel consumption and to solve a different noise (jar) which occurred when the outer pad is slid with respect to the disc so as to conspicuously improve utility value of the disc brake.
  • the more the accuracy of the manufacturing accuracy and attaching accuracy of the disc is enhanced and the more the disk is not kicked back into the outer pad, the more such an effect can be obtained.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
EP95111934A 1994-09-07 1995-07-28 Frein à disque à êtrier flottant Expired - Lifetime EP0684400B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP23951794 1994-09-07
JP239517/94 1994-09-07
JP7726295 1995-03-08
JP77262/95 1995-03-08

Publications (3)

Publication Number Publication Date
EP0684400A2 true EP0684400A2 (fr) 1995-11-29
EP0684400A3 EP0684400A3 (fr) 1995-12-27
EP0684400B1 EP0684400B1 (fr) 1999-01-27

Family

ID=26418367

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95111934A Expired - Lifetime EP0684400B1 (fr) 1994-09-07 1995-07-28 Frein à disque à êtrier flottant

Country Status (3)

Country Link
US (1) US5934416A (fr)
EP (1) EP0684400B1 (fr)
DE (1) DE69507536T2 (fr)

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US6454056B1 (en) * 2001-05-31 2002-09-24 Robert Bosch Corporation Disc brake with anti-caming and constant bearing length for guide pins
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US7721854B1 (en) 2007-03-30 2010-05-25 Robert Bosch Gmbh Assured running clearance caliper
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CN101823433A (zh) * 2010-05-21 2010-09-08 徐工集团工程机械股份有限公司科技分公司 湿式制动驱动桥及具有该驱动桥的装载机

Also Published As

Publication number Publication date
EP0684400B1 (fr) 1999-01-27
DE69507536D1 (de) 1999-03-11
DE69507536T2 (de) 1999-08-19
EP0684400A3 (fr) 1995-12-27
US5934416A (en) 1999-08-10

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